Pressure fluid generator



v 2 Sheets-Sheet 1 lll IlIllII LTER IN VEN TOR.

H. WALTER PRESSURE FLUID GENERATOR HELLMUTH WA Dec. 15, 1959 Filed May12, 1954 FIG.I

1 WALTER 2,916,377

PRESSURE FLUID GENERATOR Filed May 12, 1954 I 2 Sheets-Sheet '2 FIG. 5 L

' HELLMUTH WALTER 1N VEN TOR.

United States Patent 2,916,877 PRESSURE FLUID GENERATOR Hellmuth Walter,Upper Montclair, N..l., assignor to Worthington Corporation, Harrison,N.J., a corporation of Delaware Application May 12, 1954, Serial No.429,337 3 Claims. (Cl. 60-3955) This invention relates generally topressure fluid generators and more particularly to a pressure fluidgenerator which is in the form of an elongated combustion chamber havinga coolant in heat exchange relationship therewith to be injected intothe combustion chamber to form with the combustion products therein agas and superheated vapor working mixture at a relatively hightemperature and high pressure for application to any desired use.

Combustion flasks of various types for generating pressure fluid havebeen utilized in propulsion apparatus such as torpedos.

However, it has been found that a fluid working medium at hightemperature and high pressure can be used in commercial installationssuch as in a gas turbine prime mover or other commercial installation.

The present invention covers a pressure fluid generator of the doublecasing type including an outer pressure casing and an inner combustionchamber forming casing with cooling fluid passages therebetween so thatsimultaneous control of the temperature of the combustion products ofthe combustion chamber and preheating of the cooling fluid can besecured, and in which the structure is adapted to inject or pass thepreheated .cooling fluid into the combustion chamber to form the gas andsuperheated vapor mixture working medium at high temperature and highpressure.

It is another object of the present invention to provide an improvedburner to coact with the combustion chamber of the pressure fluidgenerator for facilitating the starting up, delivering, and mixing ofthe combustible mixture therein.

It is a still further object of the present invention to provide apressure fluid generator in which the inner casing is expandiblerelative to the outer pressure casing.

With these and other objects in view, as may appear from theaccompanying specification, the invention consists of various featuresof construction and combination of parts which will be first describedin connection with the accompanying drawings showing a pressure fluidgenerator of a preferred form embodying the invention, and the featuresforming the invention will be specifically pointed out in the. claims.

In the drawings:

Figure 1 is a vertical sectionthrough the combustion chamber showing theinvention.

Figure 2 is a side view of the pressure fluid generator broken away toshow the cooling fluid passages about the inner casing.

Figure 3 is a view taken on line 3-3 of Figure 1.

Figure 4 is a view taken on line 4-4 of Figure 1.

Figure 5 is a view taken on line 5-5 of Figure 1.

Figure 6 is a fragmentary view of the invention showing a modified formof the inner casing.

The illustrated forms of the present invention as shown in Figures 1 and6 may both be used within all the desired temperature ranges andpressures within the strength and stress of the materials forming theparticular casings. However, the form of the invention shown in Figure 1is "ice particularly adaptable to temperatures and pressure rangeswherein the combustion products or gases are at a temperature andpressure such that sufficient vaporization of the cooling fluid does notoccur in the cooling passages, while that shown in Figure 6 is adaptablefor temperatures and pressures wherein the combustion products or gasesare at temperatures and pressures at which sufficient vaporization ofthe cooling fluid does occur in the cooling passages. The control of thetemperature at the particular operating pressure being a function of thevolume of cooling fluid being utilized as will appear clear from theoperation of the pressure fluid generator as hereinafter described.Suflicient vaporization being defined as vaporization of a percentage ofthe cooling water such that flooding of the combustion chamber orinterference with the combustion operation will be avoided.

Accordingly, referring more particularly to the drawings, Figures '1, 2and 6 show that the pressure fluid generator generally designated 1includes an outer casing 2 having a substantially hollow elongatedcylindrical shaped opening at one end and narrowing into a neck portion3 at the other end thereof, and a closure member 4 for said open ormouth end connected to a flange 5 about the open end by suitablethreaded members generally designated 6 circumferentially spacedinwardly of the outer periphery of said closure member. A fluid sealingmember 7 is provided between the flange 5 and the closure member 4 toprevent leakage out of the open end of said outer pressure casing 2.

The outer pressure casing will be made of materials capable ofwithstanding high pressures.

An inner casing 8 shown in Figure 1 or an inner casing 8 shown in Figure6 is removably mounted in the outer pressure casing 2 and is held inposition through threaded means 9 which connect the inner casing to theclosure -member 4 so that it will be removable therewith on disassemblyof the pressure fluid generator.

The inner casing 8 shown in Figure 1 or 8' shown in Figure 6 aresubstantially identical. They are elongated hollow cylindrical memberswhich form combustion chambers 10 and 10' therein respectively. Theinner casings 8 and 8 and their respective combustion chambers 10 and10' differ only in that one is closed, while the other is open, thedesired form of the invention to be used depending on the range ofoperational temperatures of the issuing pressure fluid mixture.

For those temperatures and pressures where sufficient vaporization ofthe cooling fluid does not occur in the cooling passage, the combustionchamber 10 is preferably utilized. It is shown as closed at the lowerend thereof by a transversely disposed flexible member or diaphragm 11which acts as a seal member to prevent flooding of the combustionchamber, and as a means to allow for relative expansion between theinner casing 8 and the outer casing 2. As shown in Figures 1 and 3, theflexible member 11 is connected to the lower end of the inner casing bycircumferentially spaced threaded bolts 12 disposed inwardly of theperiphery thereof, and to an exhaust tube 13 which projects through anannular opening 14- in the diaphragm or flexible type member 11 byspaced bolts 15 circumferentially disposed about the annular opening 14which engages a flange 16 about the upper end of the exhaust tube 13.

The circumferentially spaced bolts 12 also act to hold an evaporatormember generally designated 17 against the lower end of the innercasing, and accordingly as shown in Figure 1 the bolts 12 extend throughan annular flat member 18 thereof to hold the evaporator 17 in position,and an annular spacer element 19 being provided to allow room forflexure of the flexible member 11 under thermal changes.

2 and the closure member 4 The evaporator 17 has a cylindrical element20 extending upwardly from the annular flat member 18 which supportsevaporator plates 21, 22 and 23 having openings 24, 25 and 26respectively therein with progressively decreasing diameters, thelowermost opening 26 being approximately the same in diameter as anexhaust passage 27 provided in the exhaust tube 13.

The flange 16 of the exhaust tube extends upwardly through an opening inthe annular flat plate 18 so that the upper end of the exhaust tube liesjust below the opening 26. In this position the flange 16 of the exhausttube is adapted to coact with the annular plate 18 to both enable theexhaust tube 13 to be removed together with the closure head 4 and innercasing 8 on disassembly of the pressure fluid chamber, and as a stopmeans to prevent undue flexure or overstressing of the flexible memberon removal.

This is accomplished by means of spaced lugs 29 projecting from theflange 16 on the exhaust tube 13 which on assembly will be passedthrough lug grooves 30 formed off the opening 28 in the annular flatplate 18 of the evaporator 17. By turning the exhaust tube 13approximately 45 degrees after assembly, the lugs 29 will act to engagethe annular fiat plate 18 when the inner casing is lifted from the outercasing on disassembly. In addition the lugs will act as an upper stopshoulder against the upper surface of the annular flat plate of theevaporator. An annular ring 31 of slightly larger diameter than theflange 16 is connected to the lower end thereof by the spaced threadedmembers 15. The annular ring 31 similarly acts as a lower stop memberwhen it engages the lower surface of the annular flat member 18.

The exhaust tube 13 is elongated so that it extends downwardly throughthe annular opening of the flexure member 11 into a bore 32 in the neckportion 3 of the outer casing 2 and in running fit engagement therewithto allow an annular shoulder 33 about the medial portion thereof tosealingly engage a seat 34 provided about the mouth of the bore 32 whicharrangement acts to seal ofl the lower end of the outer pressure casing2.

The exhaust passage 27 and the bore 32 are also in communication with adischarge outlet 35 formed in the coupling connector 36 integral withthe neck portion 3, so that pressure fluid developed in the combustionchambers 10 or 10' respectively as hereinafter described may be directedto any desired use or purpose, all of the above being clearly shown inFigures 1, 3 and 6 of the drawings.

In the form of the invention shown in Figure 6, the inner casing 8' inthe type which while adaptable to all temperatures is especiallyapplicable to those temperatures and pressures of the combustion gaswhere suflicient vaporization of the cooling fluid does occur in thecooling passages. In this form of the invention the combustion chamber10' is shown in Figure 6 as open at the lower end thereof and in directcommunication with the bore 32. Thus, working fluid generated in thecombustion chamber 10 also as hereinafter described may be directedthrough the bore 32 to the discharge outlet 35 to any desired use orpurpose.

Burner member The burner member 39, shown in Figures 1, 4 and conductsthe flow of air and fuel into the combustion chambers or 10' dependingon the form of the invention which is utilized.

' The combustion chambers 10 and 10' narrow at their upper ends into aledge 37, which ledge is of lesser diameter than the flange 38 providedabout the outer surface of the burner member 39. The burner member 39 isdisposed in the upper end of the inner casings 8 or 8 and is supportablyconnected to the closure head 4 in the approximate axial line of thecombustion chambers 10 or 10' as by threaded bushings 40 and nuts 41.The ledge acts to prevent the burner member 39 from dropping into thecombustion chamber should it be separated from this closure head 4 forany reason.

The burner member 39 used in both forms of the invention is identical.It is an annular member which depends downwardly from the closure head 4to which it is connected, as above described, so that it is in spacedrelation to whichever inner casing 8 or 8' is in use to form the annularair flow passage or chamber 42.

Gas under pressure is led to the burner 39 from any suitable source (notshown) through the main gas inlet 43 and the auxiliary gas inlet 44.Main gas inlet 43 communicates through the passage 45 formed in thethreaded bushing 40 and the connecting union 41 to an annular gasdistributing chamber 46. Circumferentially spaced bores 47 having theirinner ends communicating with the annular gas distributing chamber 46and their outer ends opening into the combustion chamber 10 or 10 toprovide means for passing the gas under pressure into whichever one ofthe combustion chambers is being used.

In order to insure ignition of the air-gas mixture during the startingup and prior to the time when the combustion mixture is brought to atemperature and pressure at which combustion will continue withoutignition, the auxiliary gas inlet 44 extends through the closure head 4to communicate with a passage 51 extending through the threaded bushing40 and connecting union 41 which has its outlet adjacent the centeropening 52 formed in the burner member.

The air inlet passages 48 and 49 are connected to a source of compressedair (not shown) and extend through the closure head 4 to communicatewith the air flow passage 42. Circumferentially spaced openings 50 onthe flange 38 act as an outlet for the air flow passage 42 and as ameans to create turbulence so that the air which enters in a ringoutwardly of the entering gas will be thoroughly mixed therewith in thecombustion chamber 10 or 10', all of the above being clearly shown inFigures 1, 4 and 5 of the drawings.

Connected in the axial line of the closure head 4 and extendingdownwardly. into the center opening 52 of the burner member is a sparkplug retainer 53. The spark retainer 53 is a hollow cylindrical memberhaving a closure end 54 at its lower end in approximate axial alignmentwith the lower end of the burner member 39 adapted to threadably receivea spark plug 55 so that the contact points 56 thereof will extend intothe entering air and fuel mixture for easy ignition thereof.

The auxiliary fuel supplied through the auxiliary fuel inlet 44 will ofcourse enter mainly through the central opening 52 which forms anannular passage with the spark plug retainer element. This brings thefuel into close proximity to the contact points 56 during the startingup and continued operation of the combustion chamber.

The spark plug 55 is connected to any suitable source of electriccurrent (not shown) through the electrical line 57 in the manner wellproven in the art. The electric line 57 is disposed inside a shield 58connected to the upper end of the spark plug 55 so that the hollowchamber formed by the end closure 54 in the spark plug retainer 53 maybe filled with a coolant to hold the temperature of the spark plug downwithout interfering with the operation of the spark plug.

Cooling means The temperature of the issuing gas mixture can becontrolled in part by the ratio of the air to fuel mixture being ignitedat a particular pressure. However, the temperature of the issuing gas isfor practical purposes a function of the volume of cooling fluidutilized. Thus the greater the volume of cooling fluid utilized, thelower the temperature of the issuing gas mixture. Conversely, where alarge volume of cooling fluid is used to lower the temperature of theissuing gas, the less preheating of the cooling fluid that will occur.Accordingly, at certain temperatures and pressures sutficientvaporization of the cooling fluid may never be reached before "it isfltobe i' ie'cted 'into the com bustion chamber as hereinafter described.

The cooling means will be the same in either form of the invention.Thus, inner casings 8 shown in Figure 1 and in Figure 6 are held inspaced relation to the outer casing 2 by horizontally and verticallyconnected fin elements 59 about the sections of the inner casing 8 and8' holding the burner member 39, and spirally disposed fins 60 about thesection of the inner casings 8 and 8 forming the combustion chambers 10and 10'. These fin elements 59 and 60 formed on the outer walls of therespective inner casings 8 and 8 taken with the inner outer casing 2form corresponding upper horizontal and vertical flow passages 61 andspiral flow passages 62 which communicate with each other through thecircumferentially disposed passages 63 in an annular horizontal fin 64between the respective elements 59 and 60.

Cooling fluid is delivered to the horizontal and vertical flow passages61 through a cooling fluid inlet 65 which is connected through asuitable conduit 66 to the discharge of a metering pump (not shown)which takes its suction from any suitable source (also not shown) sothat the cooling fluid will be forced automatically through the coolingpassages into the combustion chambers 10 and 10 despite variations ofpressure in thecombustion chambers during the starting up and operationof the pressure fluid generator.

Where the temperature of the issuing gas is maintained relatively low;that is at temperatures and pressures such that the cooling fluid is notsufficiently vaporized in the cooling passages; the cooling fluid issuesfrom the lower end of the spiral passages 62 substantially in liquidform. Then in the form of the invention shown in Figure l, the preheatedcooling fluid enters the chamber 67 formed between the lower ends of theinner casing 8 and outer casing 2, and by differential pressure will actto force and inject liquid and vapor through the communicatingcircumferentially spaced transverse passages 68 into the combustionchamber 10 where the liquid falls or drops onto the plates 21, 22 and 23of the evaporator 17. The fluid is quickly evaporated from the plates21, 22 and 23 and then superheated by direct heat exchange relation withthe combustion gases and forms therewith a gas and superheated pressurefluid Working mixture.

In the form of the invention shown in Figure 6, the cooling liquid willflow to the mixing chamber 69 where it is mixed with and completelyvaporized by the combusting gases.

When the temperature of the issuing gas is maintained relatively high;that is, at a temperature and pressure such that the cooling fluid isvaporized in some portion of the spiral passages 62, the cooling fluidissuing from the lower end of the spiral passages 62 is mainly in avapor state. Then in the form of the invention shown in Figure 1, thevaporized fluid issuing from the spiral passages 62 will pass bydifferential pressure through the circumferentially spaced transverseopenings 68 into the combustion chamber 10 where it is mixed with thecombustion products and superheated to form the pressure fluid workingmixture. While in the form of the invention shown in Figure 6, theissuing vapor from the spiral passages 62 is forced through annularpassage 70 formed by the thickened end 71 of the inner casing 8' bydiflerential pressure and ejector-like action into the mixing chamber 69where the vapors combined with the combustion products and aresuperheated to form the pressure fluid working mixture.

The pressure fluid working mixture formed in the combustion chamber 10passes through the exhaust passage 27 into the discharge outlet 35 andthe pressure fluid working mixture formed in combustion chamber 10passes through the bore 32 to the discharge outlet 35. From thedischarge outlet 35 it can be passed to any desired use.

wall of the 'is cut OH and the remaining Operation The starting up andoperational procedure same in either form of the invention. Air is firstintroduced through the air inlets 48 and 49 into either the combustionchamber 10 or 10' depending on which form of the invention is beingused. While the air is continued, a large excess of cooling fluidisdelivered to the cooling fluid passages and the combustion chambers 10or 10', as above described. The injected cooling fluid which reaches therespective combustion chambers 10 or 10 will be entrained and atomizedby the air and flow out therewith through the exhaust passage 27 or 32to the discharge outlet 35.

' After the air and cooling fluid flow are in operation, the contacts 56of the ignition means 55 are placed into operation and then the fuel isadmitted to the combustion chamber 10 or 10' through the main fuel inletand auxiliary fuel inlet 44 so that as soonas the fuel is admittedcombustion begins.

The fuel is of course adm'tted initially under relatively low pressure,as combustion continues either by reason of the back pressure producedbythe use to which the pressure fluid is put or by the manualthrottlingmeans 72, shown in Figure 2 of the drawings, or both, the pressure maybe increased. Cooling fluid and air-fuel ratio are adjustedsimultaneously therewith until the desired temperature and pressure ofthe issuing working fluid is obtained for the desired use.

During the operation of the combustion chamber as above described, thecooling fluid will also by reason of the convoluted nature of thehorizontal and vertical flow passages about the burner section of therespective inner casings 8 and 8' will be circulated at this level toprevent the burner from overheating and to absorb as much heat by heatexchange as necessary.

When it is desired to stop the operation of the combustion chambers 10or 10, the supply of fuel is cut off and the pressure fluid generator iscooled by allowing air and cooling fluid to pass therethrough. Then thecooling fluid heat coupled with air will act to dry the combustionchamber and fluid passages.

It will be understood that the invention is not to be limited to thespecific construction or arrangement of parts shown, but that they maybe widely modified within the invention defined by the claims.

What is claimed is:

1. In a pressure generator, an outer pressure casing open at one end andhaving an outlet at the end remote from said opening, a closure for saidopen end, an inner casing having a combustion chamber formed thereincommunicating with said outlet, first fastening means connecting theinner casing to the closure whereby said inner casing is adapted toexpand and contract relative to said outer casing during thermal changesand is removable with said closure on disassembly of the pressuregenerator, means on said inner casing and between said inner and saidouter casing to form cooling passages therebe tween, said coolingpassages communicating with said combustion chamber, a burner in saidinner casing having .flow passages for fuel therein connected to asource of fuel under pressure and opening into said combustion chamber,second fastening means for connecting the burner to the closure wherebysaid burner is removable with said closure, and said inner casing ondisassembly of the pressure generator, said burner forming an airflowpassage with said inner casing, inlet means connecting said air-flowpassage to a source of air under pressure, said air-flow passage andsaid fuel passage having outlets opening into said combustion chamberand disposed so that said air-flow passage outlet opens circumjacent thefuel passage outlet, an annular flange on said burner between the saidair inlet means and said air outlet openings having circumferentiallyspaced openings providing communication between said air-flow passagewill be the and said combustion chamber to create turbulence forthorough mixture between said air and gas, and means coacting with saidannular flange including a ledge formed about the upper end of saidinner casing to prevent said burner member from falling into saidcombustion chamber, an igniter means including igniter supporting meansmounted adjacent said burner to form together with said burner anannular passage connecting the air inlet means to the combustionchamber, and an auxiliary fuel port in said burner and in operativecommunication with said igniter for introducing fuel to said igniter forstart-up, inlet means in said outer casing and communicating with saidcooling passages for providing cooling fluid thereto.

2. In apressure fluid generator as claimed in claim 1 wherein saidcommunication between the cooling passages and combustion chamberinclude an annular thickened end portion on said inner casing, saidannular portion adapted to coact with the outer pressure casing to forma narrow annular restricted passage opening into the lower end of thecombustion chamber.

3. In the pressure fluid generator of claim 2 wherein said ignitersupporting means includes a retainer means connected to a source ofcooling fluid mounted thereon about said igniter for providing a coolingchamber therefor.

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